EP1416231A1 - Appareil frigorifique - Google Patents
Appareil frigorifique Download PDFInfo
- Publication number
- EP1416231A1 EP1416231A1 EP03019372A EP03019372A EP1416231A1 EP 1416231 A1 EP1416231 A1 EP 1416231A1 EP 03019372 A EP03019372 A EP 03019372A EP 03019372 A EP03019372 A EP 03019372A EP 1416231 A1 EP1416231 A1 EP 1416231A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- refrigerant
- expander
- heat exchanger
- compressor
- way valve
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/06—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point using expanders
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B9/00—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point
- F25B9/002—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant
- F25B9/008—Compression machines, plants or systems, in which the refrigerant is air or other gas of low boiling point characterised by the refrigerant the refrigerant being carbon dioxide
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B1/00—Compression machines, plants or systems with non-reversible cycle
- F25B1/10—Compression machines, plants or systems with non-reversible cycle with multi-stage compression
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
Definitions
- the present invention relates to a refrigeration cycle apparatus using carbon dioxide as refrigerant and having a compressor, an outdoor heat exchanger, an expander and an indoor heat exchanger.
- a flow rate of refrigerant which circulates through a refrigeration cycle apparatus is all the same in any points in a refrigeration cycle. If a suction density of refrigerant passing through a compressor is defined as DC and a suction density of refrigerant passing through an expander is defined as DE, the DE/DC (density ratio) is always constant.
- CO 2 refrigerant carbon dioxide (CO 2 hereinafter) in which ozone destroy coefficient is zero and global warming coefficient is extremely smaller than Freon.
- the CO 2 refrigerant has a low critical temperature as low as 31.06°C.
- a high pressure side (outlet of the compressor - gas cooler - inlet of pressure reducing device) of the refrigeration cycle apparatus is brought into a supercritical state in which CO 2 refrigerant is not condensed, and there is a feature that operation efficiency of the refrigeration cycle apparatus is deteriorated as compared with a conventional refrigerant. Therefore, it is important for the refrigeration cycle apparatus using CO 2 refrigerant to maintain optimal COP, and if an operating condition is changed, it is necessary to obtain an operating state (pressure and temperature of the refrigerant) which is optimal to this operating condition.
- the number of rotation of the expander and the number of rotation of the compressor must be the same, and in the expander which is designed optimally with a predetermined density ratio, it is difficult to maintain the optimal COP when the operation condition is changed.
- the power recover by the expander is used as a driving force for an auxiliary compressor which is different from the compressor, it is possible to eliminate the constraint that the number of rotation of the expander and the number of rotation of the compressor must be the same. However, even if the auxiliary compressor is driven by the expander, the constraint that the density ratio is constant is still remained, and it is still necessary to control the amount of refrigerant which flows into the expander.
- a first aspect of the present invention provides a refrigeration cycle apparatus using carbon dioxide as refrigerant and having a compressor, an outdoor heat exchanger, an expander and an indoor heat exchanger, wherein an injection circuit for introducing high pressure refrigerant is provided in a halfway of an expansion process of said expander.
- the apparatus further comprises an adjusting valve for adjusting an amount of refrigerant from the injection circuit.
- an adjusting valve for adjusting an amount of refrigerant from the injection circuit.
- the expander is provided at its refrigerant-inflow side with a pre-expansion valve.
- a pre-expansion valve When it is necessary to reduce the amount of refrigerant without changing the number of rotation of the expander, it is possible to reduce the flow rate of refrigerant per one expansion process by reducing the opening of the pre-expansion valve.
- the expander is provided at its refrigerant-inflow side with a sub-expander.
- a sub-expander By pre-expansion is carried out by the sub-expander, it is possible to adjust a state of refrigerant in the inlet of the expander, and to optimally adjust the amount of refrigerant flowing through the expander. Therefore, it is possible to efficiently recover power in the expander, and to recover the expansion power also in the sub-expander which carries out the pre-expansion.
- the expander is provided at its refrigerant-outflow side with a sub-expander. It is possible to additionally expand by the sub-expander, and to optimally control the pressure in the outlet of the expander. Therefore, it is possible to efficiently recover power in the expander, and to recover the expansion power also in the sub-expander which carries out the additional expansion.
- an electric generator is connected to the sub-expander.
- power recover by the expander can be used for driving the compressor.
- the compressor is provided at its suction side or discharge side with an auxiliary compressor, and power recover by the expander can be used as power for driving the auxiliary compressor.
- the apparatus further comprises a first four-way valve to which a discharge side pipe and a suction side pipe of the compressor are connected, and a second four-way valve to which a discharge side pipe and a suction side pipe of the expander are connected, and refrigerant discharged from the compressor is selectively allowed to flow into the indoor heat exchanger or the outdoor heat exchanger by the first four-way valve, a direction of refrigerant flowing through the expander is always set in the same direction by the second four-way valve.
- the first to fifth aspects can be utilized as a cooling and heating air conditioner.
- the apparatus further comprises a first four-way valve to which discharge side pipes and suction side pipes of the compressor and the auxiliary compressor are connected, and a second four-way valve to which a discharge side pipe and a suction side pipe of the expander are connected, and refrigerant discharged from the compressor and the auxiliary compressor is selectively allowed to flow into the indoor heat exchanger or the outdoor heat exchanger by the first four-way valve, a direction of refrigerant flowing through the expander and the sub-expander is always set in the same direction by the second four-way valve. Therefore, the eighth aspect can be utilized as a cooling and heating air conditioner.
- Fig. 1 shows a structure of the heat pump type air conditioner of the present embodiment.
- the heat pump type air conditioner of this embodiment uses CO 2 refrigerant as refrigerant, and has refrigerant circuit.
- the refrigerant circuit comprises a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6 and an indoor heat exchanger 8 which are all connected to one another through pipes.
- the expander 6 is provided at its inflow side with a pre-expansion valve 5.
- the refrigerant circuit is provided with an injection circuit 20.
- the injection circuit 20 introduces high pressure refrigerant on the side of an outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the compressor 1 are connected to each other, and the compressor 1 utilizes power recover by the expander 6 for driving.
- Refrigerant is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12.
- the refrigerant is discharged and introduced into the outdoor heat exchanger 3.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the pre-expansion valve 5 and the expander 6, and is expanded by the pre-expansion valve 5 and the expander 6. Power recover by the expander 6 at the time of expansion is used for driving the compressor 1.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is drawn into the compressor 1.
- the flow rate of refrigerant in one expansion process by controlling the amount of refrigerant from the injection circuit 20. If the flow rate of refrigerant flowing into the expander 6 is greater than a designed flow rate, the opening of the pre-expansion valve 5 is reduced to reduce the density and it is possible to reduce the flow rate of refrigerant flowing into the expander 6. Therefore, it is possible to efficiently recover power in the expander 6 and to more efficiently recover power from the refrigeration cycle.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 2 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6 and an indoor heat exchanger 8 are connected to one another through pipes.
- the expander 6 is provided at its inflow side with a pre-expansion valve 5.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the compressor 1 are connected to each other, and the compressor 1 utilizes power recover by the expander 6 for driving.
- the refrigerant circuit includes a first four-way valve 2 to which a discharge side pipe and a suction side pipe of the compressor 1 are connected, and a second four-way valve 4 to which a suction side pipe of the pre-expansion valve 5, a discharge side pipe of the expander 6 and the injection circuit 20 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the pre-expansion valve 5 and the expander 6 and is expanded by the pre-expansion valve 5 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the compressor 1.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation.
- the CO 2 refrigerant is introduced into the pre-expansion valve 5 and the expander 6, and is expanded by the pre-expansion valve 5 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the compressor 1.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- the apparatus can efficiently be recovered in the expander 6, and more power can be recovered from the refrigeration cycle, and since the apparatus includes the first four-way valve 2 and the second four-way valve 4, the apparatus can be utilized as a cooling and heating air conditioner.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 3 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6 and an indoor heat exchanger 8 are connected to one another through pipes.
- the expander 6 is provided at its inflow side with a sub-expander 23, and an electric generator 24 is connected to a drive shaft of the sub-expander 23.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the compressor 1 are connected to each other, and the compressor 1 utilizes power recover by the expander 6 for driving.
- the refrigerant circuit includes a first four-way valve 2 to which a discharge side pipe and a suction side pipe of the compressor 1 are connected, and a second four-way valve 4 to which a suction side pipe of the sub-expander 23 and a discharge side pipe of the expander 6 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the sub-expander 23 and the expander 6 and is expanded by the sub-expander 23 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the compressor 1.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expansion device 23 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation.
- the CO 2 refrigerant is introduced into the sub-expander 23 and the expander 6, and is expanded by the sub-expander 23 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the compressor 1.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 4 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6 and an indoor heat exchanger 8 are connected to one another through pipes.
- the expander 6 is provided at its discharge side with a sub-expander 23, and an electric generator 24 is connected to a drive shaft of the sub-expander 23.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the compressor 1 are connected to each other, and the compressor 1 utilizes power recover by the expander 6 for driving.
- the refrigerant circuit includes a first four-way valve 2 to which a discharge side pipe and a suction side pipe of the compressor 1 are connected, and a second four-way valve 4 to which a discharge side pipe of the sub-expander 23, an inflow side pipe of the expander 6 and the injection circuit 20 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the expander 6 and the sub-expander 23 and is expanded by the expander 6 and the sub-expander 23. Power recover by the expander 6 at the time of expanding operation is used for driving the compressor 1.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. In this case, torque of the electric generator 24 (load of the electric generator) is minimized.
- the adjusting valve 7 is closed, and torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation.
- the CO 2 refrigerant is introduced into the expander 6 and the sub-expander 23, and is expanded by the expander 6 and the sub-expander 23. Power recover by the expander 6 at the time of expanding operation is used for driving the compressor 1.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. In this case, torque of the electric generator 24 (load of the electric generator) is minimized.
- the adjusting valve 7 is closed and torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 5 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6, an indoor heat exchanger 8 and an auxiliary compressor 10 are connected to one another through pipes.
- the expander 6 is provided at its inflow side with a pre-expansion valve 5.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit includes a first four-way valve 2 to which a discharge side pipe of the compressor 1 and a suction side pipe of the auxiliary compressor 10 are connected, and a second four-way valve 4 to which a suction side pipe of the pre-expansion valve 5, a discharge side pipe of the expander 6 and the injection circuit 20 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the pre-expansion valve 5 and the expander 6 and is expanded by the pre-expansion valve 5 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the first four-way valve 2 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation. Then, the CO 2 refrigerant is introduced into the pre-expansion valve 5 and the expander 6, and is expanded by the pre-expansion valve 5 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the first four-way valve 2 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 6 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6, an indoor heat exchanger 8 and an auxiliary compressor 10 are connected to one another through pipes.
- the expander 6 is provided at its inflow side with a sub-expander 23, and an electric generator 24 is connected to a drive shaft of the sub-expander 23.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit includes a first four-way valve 2 to which a discharge side pipe of the compressor 1 and a suction side pipe of the auxiliary compressor 10 are connected, and a second four-way valve 4 to which a suction side pipe of the sub-expander 23, a discharge side pipe of the expander 6 and the injection circuit 20 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the sub-expander 23 and the expander 6 and is expanded by the sub-expander 23 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the first four-way valve 2 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation. Then, the CO 2 refrigerant is introduced into the sub-expander 23 and the expander 6, and is expanded by the sub-expander 23 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the first four-way valve 2 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 7 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6, an indoor heat exchanger 8 and an auxiliary compressor 10 are connected to one another through pipes.
- the expander 6 is provided at its discharge side with a sub-expander 23, and an electric generator 24 is connected to a drive shaft of the sub-expander 23.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit includes a first four-way valve 2 to which a discharge side pipe of the compressor 1 and a suction side pipe of the auxiliary compressor 10 are connected, and a second four-way valve 4 to which a discharge side pipe of the sub-expander 23, an inflow side pipe of the expander 6 and the injection circuit 20 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the expander 6 and the sub-expander 23 and is expanded by the expander 6 and the sub-expander 23. Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. In this case, torque of the electric generator 24 (load of the electric generator) is minimized.
- the adjusting valve 7 is closed and torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the first four-way valve 2 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation.
- the CO 2 refrigerant is introduced into the expander 6 and the sub-expander 23, and is expanded by the expander 6 and the sub-expander 23. Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6.
- the adjusting valve 7 is closed and torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the first four-way valve 2 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 8 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an auxiliary compressor 10, an outdoor heat exchanger 3, an expander 6 and an indoor heat exchanger 8 are connected to one another through pipes.
- the expander 6 is provided at its inflow side with a pre-expansion valve 5.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit includes a first four-way valve 2 to which a suction side pipe of the compressor 1 and a discharge side pipe of the auxiliary compressor 10 are connected, and a second four-way valve 4 to which a suction side pipe of the pre-expansion valve 5, a discharge side pipe of the expander 6 and the injection circuit 20 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 and further super-pressurized by the auxiliary compressor 10 and then, is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water.
- the CO 2 refrigerant is introduced into the pre-expansion valve 5, the expander 6 and the sub-expander 21 and is expanded by the pre-expansion valve 5, the expander 6 and the sub-expander 21.
- Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like.
- the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 and further super-pressurized by the auxiliary compressor 10 and then, is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation.
- the CO 2 refrigerant is introduced into the pre-expansion valve 5, the expander 6 and the sub-expander 21 and is expanded by the pre-expansion valve 5, the expander 6 and the sub-expander 21.
- Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like.
- the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 9 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an auxiliary compressor 10, an outdoor heat exchanger 3, an expander 6 and an indoor heat exchanger 8 are connected to one another through pipes.
- the expander 6 is provided at its inflow side with a sub-expander 23, and an electric generator 24 is connected to a drive shaft of the sub-expander 23.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit includes a first four-way valve 2 to which a suction side pipe of the compressor 1 and a discharge side pipe of the auxiliary compressor 10 are connected, and a second four-way valve 4 to which a suction side pipe of the sub-expander 23, a discharge side pipe of the expander 6 and the injection circuit 20 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 and further super-pressurized by the auxiliary compressor 10 and then, is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the sub-expander 23 and the expander 6 and is expanded by the sub-expander 23 and the expander 6.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 and further super-pressurized by the auxiliary compressor 10 and then, is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation. Then, the CO 2 refrigerant is introduced into the sub-expander 23 and the expander 6 and is expanded by the sub-expander 23 and the expander 6.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 10 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an auxiliary compressor 10, an outdoor heat exchanger 3, an expander 6 and an indoor heat exchanger 8 are connected to one another through pipes.
- the expander 6 is provided at its discharge side with a sub-expander 23, and an electric generator 24 is connected to a drive shaft of the sub-expander 23.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit includes a first four-way valve 2 to which a suction side pipe of the compressor 1 and a discharge side pipe of the auxiliary compressor 10 are connected, and a second four-way valve 4 to which a discharge side pipe of the sub-expander 23, an inflow side pipe of the expander 6 and the injection circuit 20 are connected.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 and further super-pressurized by the auxiliary compressor 10 and then, is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the expander 6 and the sub-expander 23 and is expanded by the expander 6 and the sub-expander 23.
- Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. In this case, torque of the electric generator 24 (load of the electric generator) is minimized.
- the adjusting valve 7 is closed and the electric generator 24 is connected to the sub-expander 23 to reduced the low pressure side pressure, thereby reducing the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 and further super-pressurized by the auxiliary compressor 10 and then, is introduced into the indoor heat exchanger 8 through the first four-way valve 2.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation. Then, the CO 2 refrigerant is introduced into the expander 6 and the sub-expander 23 and is expanded by the expander 6 and the sub-expander 23.
- Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. In this case, torque of the electric generator 24 (load of the electric generator) is minimized.
- the adjusting valve 7 is closed, and torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 11 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6, an indoor heat exchanger 8 and an auxiliary compressor 10 are connected to one another through pipes.
- the expander 6 is provided at its inflow side with a pre-expansion valve 5.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit comprises a first four-way valve 2 to which a discharge side pipe and a suction side pipe of the compressor 1 are connected, a second four-way valve 4 to which a discharge side pipe and a suction side pipe of the expander 6 and the injection circuit 20 are connected, and a third four-way valve 9 to which a discharge side pipe and a suction side pipe of the auxiliary compressor 10 are connected.
- the first four-way valve 2 and the third four-way valve 9 are switched over so that the discharge side of the auxiliary compressor 10 becomes the suction side of the compressor 1.
- the first four-way valve 2 and the third four-way valve 9 are switched over so that the discharge side of the compressor 1 becomes the suction side of the auxiliary compressor 10.
- the second four-way valve 4 By switching the second four-way valve 4, a direction of the refrigerant flowing through the expander 6 becomes always the same direction.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the pre-expansion valve 5, the expander 6 and the sub-expander 21 and is expanded by the pre-expansion valve 5, the expander 6 and the sub-expander 21.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the third four-way valve 9 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 through the first four-way valve 2 and the third four-way valve 9 and further super-pressurized by the auxiliary compressor 10.
- the refrigerant whose pressure was increased by the auxiliary compressor 10 is introduced into the indoor heat exchanger 8 through the third four-way valve 9.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation.
- the CO 2 refrigerant is introduced into the pre-expansion valve 5, the expander 6 and the sub-expander 21 and is expanded by the pre-expansion valve 5, the expander 6 and the sub-expander 21.
- Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like.
- the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the opening of the pre-expansion valve 5 is reduced to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the pre-expansion valve 5 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- the compressor 1 which compresses refrigerant and the expander 6 and the auxiliary compressor 10 which recover the power are separated from each other.
- the refrigeration cycle is switched such that the refrigerant is supercharged by the auxiliary compressor 10 at the time of the cooling operation mode, and the refrigerant is super-pressurized at the time of the heating operation mode.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 12 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6, an indoor heat exchanger 8 and an auxiliary compressor 10 are connected to one another through pipes.
- the expander 6 is provided at its inflow side with a sub-expander 23, and an electric generator 24 is connected to a drive shaft of the sub-expander 23.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit comprises a first four-way valve 2 to which a discharge side pipe and a suction side pipe of the compressor 1 are connected, a second four-way valve 4 to which a discharge side pipe and a suction side pipe of the expander 6 and the injection circuit 20 are connected, and a third four-way valve 9 to which a discharge side pipe and a suction side pipe of the auxiliary compressor 10 are connected.
- the first four-way valve 2 and the third four-way valve 9 are switched over so that the discharge side of the auxiliary compressor 10 becomes the suction side of the compressor 1.
- the first four-way valve 2 and the third four-way valve 9 are switched over so that the discharge side of the compressor 1 becomes the suction side of the auxiliary compressor 10.
- the second four-way valve 4 By switching the second four-way valve 4, a direction of the refrigerant flowing through the expander 6 becomes always the same direction.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the sub-expander 23 and the expander 6 and is expanded by the sub-expander 23 and the expander 6. Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the third four-way valve 9 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 through the first four-way valve 2 and the third four-way valve 9 and further super-pressurized by the auxiliary compressor 10.
- the refrigerant whose pressure was increased by the auxiliary compressor 10 is introduced into the indoor heat exchanger 8 through the third four-way valve 9.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation.
- the CO 2 refrigerant is introduced into the sub-expander 23 and the expander 6 and is expanded by the sub-expander 23 and the expander 6.
- Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like.
- the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- the compressor 1 which compresses refrigerant and the expander 6 and the auxiliary compressor 10 which recover the power are separated from each other.
- the refrigeration cycle is switched such that the refrigerant is supercharged by the auxiliary compressor 10 at the time of the cooling operation mode, and the refrigerant is super-pressurized at the time of the heating operation mode.
- a refrigeration cycle apparatus according to another embodiment of the present invention will be explained with reference to the drawing based on a heat pump type cooling and heating air conditioner.
- Fig. 13 shows a structure of the heat pump type cooling and heating air conditioner of this embodiment.
- the heat pump type cooling and heating air conditioner of this embodiment uses a CO 2 refrigerant as refrigerant, and comprises a refrigerant circuit in which a compressor 1 having a motor 12, an outdoor heat exchanger 3, an expander 6, an indoor heat exchanger 8 and an auxiliary compressor 10 are connected to one another through pipes.
- the expander 6 is provided at its discharge side with a sub-expander 23, and an electric generator 24 is connected to a drive shaft of the sub-expander 23.
- the refrigerant circuit is provided with an injection circuit 20 which introduces high pressure refrigerant on the side of the outlet of the outdoor heat exchanger 3 in a halfway of the expansion process of the expander 6.
- the injection circuit 20 is provided with an adjusting valve 7 which adjusts an amount of refrigerant flowing through the injection circuit 20.
- a drive shaft of the expander 6 and a drive shaft of the auxiliary compressor 10 are connected to each other, and the auxiliary compressor 10 is driven by power recover by the expander 6.
- the refrigerant circuit comprises a first four-way valve 2 to which a discharge side pipe and a suction side pipe of the compressor 1 are connected, a second four-way valve 4 to which a discharge side pipe and a suction side pipe of the expander 6 and the injection circuit 20 are connected, and a third four-way valve 9 to which a discharge side pipe and a suction side pipe of the auxiliary compressor 10 are connected.
- the first four-way valve 2 and the third four-way valve 9 are switched over so that the discharge side of the auxiliary compressor 10 becomes the suction side of the compressor 1.
- the first four-way valve 2 and the third four-way valve 9 are switched over so that the discharge side of the compressor 1 becomes the suction side of the auxiliary compressor 10.
- the second four-way valve 4 By switching the second four-way valve 4, a direction of the refrigerant flowing through the expander 6 becomes always the same direction.
- Refrigerant at the time of the cooling operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the outdoor heat exchanger 3 through the first four-way valve 2.
- the outdoor heat exchanger 3 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. Then, the CO 2 refrigerant is introduced into the expander 6 and the sub-expander 23 and is expanded by the expander 6 and the sub-expander 23. Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the outdoor heat exchanger 3, the number of rotation of the compressor 1 and the like. If the flow rate of the refrigerant is smaller than the calculated optimal refrigerant amount, the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. In this case, the torque of the electric generator 24 (load of the electric generator) is minimized.
- the adjusting valve 7 is closed and torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the indoor heat exchanger 8 through the second four-way valve 4 and is evaporated and suctions heat in the indoor heat exchanger 8. A room is cooled by this endotherm.
- the refrigerant which has been evaporated is introduced into the auxiliary compressor 10 through the third four-way valve 9 and supercharged by the auxiliary compressor 10, and drawn into the compressor 1.
- Refrigerant at the time of the heating operation mode is compressed at a high temperature and under a high pressure by the compressor 1 which is driven by the motor 12 and is discharged.
- the refrigerant is introduced into the auxiliary compressor 10 through the first four-way valve 2 and the third four-way valve 9 and further super-pressurized by the auxiliary compressor 10.
- the refrigerant whose pressure was increased by the auxiliary compressor 10 is introduced into the indoor heat exchanger 8 through the third four-way valve 9.
- the indoor heat exchanger 8 since CO 2 refrigerant is in a supercritical state, the refrigerant is not brought into two-phase state, and dissipates heat to outside fluid such as air and water. A room is heated utilizing this radiation.
- the CO 2 refrigerant is introduced into the expander 6 and the sub-expander 23 and is expanded by the expander 6 and the sub-expander 23.
- Power recover by the expander 6 at the time of expanding operation is used for driving the auxiliary compressor 10.
- an optimal amount of refrigerant flowing into the expander 6 is calculated from a high pressure refrigerant temperature, a high pressure refrigerant pressure and a refrigerant evaporation pressure detected on the side of the outlet of the indoor heat exchanger 8, the number of rotation of the compressor 1 and the like.
- the opening of the adjusting valve 7 is increased to increase the amount of refrigerant which is allowed to flow into the injection circuit 20, thereby increasing the amount of refrigerant per one expansion process of the expander 6. In this case, the torque of the electric generator 24 (load of the electric generator) is minimized. If the flow rate of refrigerant is greater than the calculated optimal refrigerant amount, the adjusting valve 7 is closed and torque of the electric generator 24 (load of the electric generator) is increased to reduce the flow rate of refrigerant flowing into an inlet of the expander 6.
- the CO 2 refrigerant expanded by the sub-expander 23 and the expander 6 is introduced into the outdoor heat exchanger 3 through the second four-way valve 4 and is evaporated and suctions heat in the outdoor heat exchanger 3.
- the refrigerant which has been evaporated is drawn into the compressor 1 through the first four-way valve 2.
- the compressor 1 which compresses refrigerant and the expander 6 and the auxiliary compressor 10 which recover the power are separated from each other.
- the refrigeration cycle is switched such that the refrigerant is supercharged by the auxiliary compressor 10 at the time of the cooling operation mode, and the refrigerant is super-pressurized at the time of the heating operation mode.
- the present invention can also be applied to other refrigeration cycle apparatuses in which the outdoor heat exchanger 3 is used as a first heat exchanger, the indoor heat exchanger 8 is used as a second heat exchanger, and the first and second heat exchangers are utilized for hot and cool water devices or thermal storages.
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Mechanical Engineering (AREA)
- Thermal Sciences (AREA)
- General Engineering & Computer Science (AREA)
- Chemical Kinetics & Catalysis (AREA)
- Chemical & Material Sciences (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
- Sorption Type Refrigeration Machines (AREA)
- Air-Conditioning For Vehicles (AREA)
- Devices That Are Associated With Refrigeration Equipment (AREA)
- Crystals, And After-Treatments Of Crystals (AREA)
- Polarising Elements (AREA)
- Inorganic Insulating Materials (AREA)
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2002318129A JP3863480B2 (ja) | 2002-10-31 | 2002-10-31 | 冷凍サイクル装置 |
JP2002318129 | 2002-10-31 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1416231A1 true EP1416231A1 (fr) | 2004-05-06 |
EP1416231B1 EP1416231B1 (fr) | 2008-05-14 |
Family
ID=32089586
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP03019372A Expired - Lifetime EP1416231B1 (fr) | 2002-10-31 | 2003-08-27 | Appareil frigorifique |
Country Status (6)
Country | Link |
---|---|
US (2) | US6880357B2 (fr) |
EP (1) | EP1416231B1 (fr) |
JP (1) | JP3863480B2 (fr) |
AT (1) | ATE395564T1 (fr) |
DE (1) | DE60320918D1 (fr) |
DK (1) | DK1416231T3 (fr) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP2142860A1 (fr) * | 2007-03-16 | 2010-01-13 | Carrier Corporation | Système réfrigérant à expanseur de capacité variable |
US7730741B2 (en) | 2004-07-07 | 2010-06-08 | Daikin Industries, Ltd. | Refrigeration apparatus with expander control for improved coefficient of performance |
EP2251621A1 (fr) * | 2008-02-06 | 2010-11-17 | Daikin Industries, Ltd. | Dispositif de réfrigération |
EP2439466A1 (fr) * | 2009-06-02 | 2012-04-11 | Mitsubishi Electric Corporation | Dispositif à cycle de réfrigération |
CN105423613A (zh) * | 2015-12-23 | 2016-03-23 | 广西大学 | 一种机械增压式太阳能喷射制冷***及方法 |
EP2090746B1 (fr) * | 2006-12-08 | 2019-01-23 | Daikin Industries, Ltd. | Appareil de congélation et détendeur |
Families Citing this family (24)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP4375171B2 (ja) * | 2004-08-31 | 2009-12-02 | ダイキン工業株式会社 | 冷凍装置 |
US20060080988A1 (en) * | 2004-10-20 | 2006-04-20 | Carrier Corporation | Gas cooler configuration integrated into heat pump chassis |
KR100677266B1 (ko) * | 2005-02-17 | 2007-02-02 | 엘지전자 주식회사 | 냉난방 동시형 멀티 에어컨 |
JP4552721B2 (ja) * | 2005-03-25 | 2010-09-29 | ダイキン工業株式会社 | 冷凍装置 |
JP4650049B2 (ja) * | 2005-03-25 | 2011-03-16 | ダイキン工業株式会社 | 冷凍装置 |
JP2006284086A (ja) * | 2005-03-31 | 2006-10-19 | Daikin Ind Ltd | 冷凍装置 |
JP4581795B2 (ja) * | 2005-03-31 | 2010-11-17 | ダイキン工業株式会社 | 冷凍装置 |
JP4940632B2 (ja) * | 2005-11-08 | 2012-05-30 | ダイキン工業株式会社 | ヒートポンプ給湯装置 |
JP4736727B2 (ja) * | 2005-11-11 | 2011-07-27 | ダイキン工業株式会社 | ヒートポンプ給湯装置 |
JP2009052752A (ja) * | 2005-12-19 | 2009-03-12 | Panasonic Corp | 冷凍サイクル装置 |
WO2008044456A1 (fr) | 2006-10-11 | 2008-04-17 | Panasonic Corporation | Dispositif d'expansion rotatif |
WO2008054380A2 (fr) * | 2006-10-27 | 2008-05-08 | Carrier Corporation | Cycle frigorifique économisé au moyen d'un détendeur |
JP4991255B2 (ja) * | 2006-11-22 | 2012-08-01 | 日立アプライアンス株式会社 | 冷凍サイクル装置 |
JP4821599B2 (ja) * | 2006-12-26 | 2011-11-24 | 株式会社富士通ゼネラル | 冷媒回路 |
WO2009101818A1 (fr) * | 2008-02-15 | 2009-08-20 | Panasonic Corporation | Appareil à cycle de réfrigération |
ES2424137T5 (es) * | 2008-08-19 | 2020-02-26 | Abb Schweiz Ag | Sistema de almacenamiento de energía termoeléctrica y procedimiento para almacenar energía termoeléctrica |
WO2010137120A1 (fr) * | 2009-05-26 | 2010-12-02 | 三菱電機株式会社 | Dispositif d'alimentation en eau chaude du type pompe à chaleur |
US8327651B2 (en) * | 2009-07-07 | 2012-12-11 | Hamilton Sundstrand Corporation | Transcritical fluid cooling for aerospace applications |
GB2474259A (en) * | 2009-10-08 | 2011-04-13 | Ebac Ltd | Vapour compression refrigeration circuit |
EP2551613B1 (fr) * | 2010-03-25 | 2017-10-11 | Mitsubishi Electric Corporation | Appareil de cycle frigorifique et procédé de fonctionnement associé |
GB201012743D0 (en) * | 2010-07-29 | 2010-09-15 | Isentropic Ltd | Valves |
CN106855107A (zh) * | 2015-12-09 | 2017-06-16 | 熵零技术逻辑工程院集团股份有限公司 | 气体变速器 |
EP3670853A1 (fr) * | 2018-12-17 | 2020-06-24 | CTB Clean Tech Brokers IVS | Appareil de pompe à chaleur et réseau de chauffage urbain comprenant un appareil de pompe à chaleur |
US20220307736A1 (en) * | 2021-03-23 | 2022-09-29 | Emerson Climate Technologies, Inc. | Heat-Pump System With Multiway Valve |
Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH386459A (de) * | 1961-10-04 | 1965-01-15 | Sulzer Ag | Einrichtung zur Kühlung gasförmiger Medien |
US4063417A (en) * | 1976-02-04 | 1977-12-20 | Carrier Corporation | Power generating system employing geothermally heated fluid |
JPS63231138A (ja) * | 1987-03-19 | 1988-09-27 | 株式会社デンソー | 冷凍装置 |
EP0635673A1 (fr) * | 1993-07-22 | 1995-01-25 | Ormat Industries, Ltd. | Système de réduction de pression avec récupération d'énergie |
JP2000234814A (ja) | 1999-02-17 | 2000-08-29 | Aisin Seiki Co Ltd | 蒸気圧縮式冷凍装置 |
JP2001116371A (ja) | 1999-10-20 | 2001-04-27 | Daikin Ind Ltd | 空気調和装置 |
US6321564B1 (en) * | 1999-03-15 | 2001-11-27 | Denso Corporation | Refrigerant cycle system with expansion energy recovery |
Family Cites Families (20)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2515825A (en) * | 1945-03-16 | 1950-07-18 | Carrier Corp | Single stage refrigeration utilizing holdover means |
US2499404A (en) * | 1946-06-08 | 1950-03-07 | Specialties Dev Corp | Liquefied gas storage and supply |
US3144316A (en) * | 1960-05-31 | 1964-08-11 | Union Carbide Corp | Process and apparatus for liquefying low-boiling gases |
US4326388A (en) * | 1980-05-05 | 1982-04-27 | Mcfee Richard | Dual open cycle heat pump and engine |
US4321801A (en) * | 1981-01-26 | 1982-03-30 | Collard Jr Thomas H | Jet operated heat pump |
US4595344A (en) * | 1982-09-30 | 1986-06-17 | Briley Patrick B | Ejector and method of controlling same |
JPH03286968A (ja) * | 1990-03-31 | 1991-12-17 | Aisin Seiki Co Ltd | 極低温冷凍装置 |
US5181376A (en) * | 1990-08-10 | 1993-01-26 | Fluor Corporation | Process and system for producing power |
US5327745A (en) * | 1993-09-28 | 1994-07-12 | The United States Of America As Represented By The Secretary Of The Navy | Malone-Brayton cycle engine/heat pump |
JPH11101520A (ja) * | 1997-09-29 | 1999-04-13 | Sharp Corp | エアサイクル式空気調和装置 |
US6138457A (en) * | 1998-02-27 | 2000-10-31 | Applied Power Technology Incorporated | Combustion powered cooling system |
JP3473436B2 (ja) * | 1998-09-16 | 2003-12-02 | 株式会社豊田自動織機 | 燃料電池装置 |
US6381973B1 (en) * | 1999-10-04 | 2002-05-07 | Delphi Technologies, Inc. | Vehicle air cycle air conditioning system |
EP1589301B1 (fr) * | 2000-03-15 | 2017-06-14 | Denso Corporation | Système à cycle d'éjection avec pression critique du fluide frigorigène |
JP4396004B2 (ja) * | 2000-07-06 | 2010-01-13 | 株式会社デンソー | エジェクタサイクル |
US6343482B1 (en) * | 2000-10-31 | 2002-02-05 | Takeshi Endo | Heat pump type conditioner and exterior unit |
ES2274021T3 (es) * | 2001-02-20 | 2007-05-16 | Thomas E. Kasmer | Bomba de calor de hydristor. |
JP4639541B2 (ja) * | 2001-03-01 | 2011-02-23 | 株式会社デンソー | エジェクタを用いたサイクル |
JP4032875B2 (ja) * | 2001-10-04 | 2008-01-16 | 株式会社デンソー | エジェクタサイクル |
JP3818115B2 (ja) * | 2001-10-04 | 2006-09-06 | 株式会社デンソー | エジェクタサイクル |
-
2002
- 2002-10-31 JP JP2002318129A patent/JP3863480B2/ja not_active Expired - Fee Related
-
2003
- 2003-08-27 AT AT03019372T patent/ATE395564T1/de not_active IP Right Cessation
- 2003-08-27 DK DK03019372T patent/DK1416231T3/da active
- 2003-08-27 EP EP03019372A patent/EP1416231B1/fr not_active Expired - Lifetime
- 2003-08-27 DE DE60320918T patent/DE60320918D1/de not_active Expired - Lifetime
- 2003-09-09 US US10/657,180 patent/US6880357B2/en not_active Ceased
-
2007
- 2007-04-18 US US11/785,569 patent/USRE43312E1/en not_active Expired - Fee Related
Patent Citations (7)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CH386459A (de) * | 1961-10-04 | 1965-01-15 | Sulzer Ag | Einrichtung zur Kühlung gasförmiger Medien |
US4063417A (en) * | 1976-02-04 | 1977-12-20 | Carrier Corporation | Power generating system employing geothermally heated fluid |
JPS63231138A (ja) * | 1987-03-19 | 1988-09-27 | 株式会社デンソー | 冷凍装置 |
EP0635673A1 (fr) * | 1993-07-22 | 1995-01-25 | Ormat Industries, Ltd. | Système de réduction de pression avec récupération d'énergie |
JP2000234814A (ja) | 1999-02-17 | 2000-08-29 | Aisin Seiki Co Ltd | 蒸気圧縮式冷凍装置 |
US6321564B1 (en) * | 1999-03-15 | 2001-11-27 | Denso Corporation | Refrigerant cycle system with expansion energy recovery |
JP2001116371A (ja) | 1999-10-20 | 2001-04-27 | Daikin Ind Ltd | 空気調和装置 |
Non-Patent Citations (3)
Title |
---|
JOO SEOK BAEK ET AL: "TRANSCRITICAL CO2 CYCLE TECHNOLOGY", SAE AUTOMOTIVE ALTERNATE REFRIGERANT SYSTEMS SYMPOSIUM, XX, XX, July 2002 (2002-07-01), pages 1 - 17, XP001169127 * |
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 11 3 January 2001 (2001-01-03) * |
PATENT ABSTRACTS OF JAPAN vol. 2000, no. 21 3 August 2001 (2001-08-03) * |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US7730741B2 (en) | 2004-07-07 | 2010-06-08 | Daikin Industries, Ltd. | Refrigeration apparatus with expander control for improved coefficient of performance |
EP2090746B1 (fr) * | 2006-12-08 | 2019-01-23 | Daikin Industries, Ltd. | Appareil de congélation et détendeur |
EP2142860A1 (fr) * | 2007-03-16 | 2010-01-13 | Carrier Corporation | Système réfrigérant à expanseur de capacité variable |
EP2142860A4 (fr) * | 2007-03-16 | 2012-06-06 | Carrier Corp | Système réfrigérant à expanseur de capacité variable |
EP2251621A1 (fr) * | 2008-02-06 | 2010-11-17 | Daikin Industries, Ltd. | Dispositif de réfrigération |
EP2251621A4 (fr) * | 2008-02-06 | 2014-05-14 | Daikin Ind Ltd | Dispositif de réfrigération |
EP2439466A1 (fr) * | 2009-06-02 | 2012-04-11 | Mitsubishi Electric Corporation | Dispositif à cycle de réfrigération |
EP2439466A4 (fr) * | 2009-06-02 | 2012-10-17 | Mitsubishi Electric Corp | Dispositif à cycle de réfrigération |
US8511112B2 (en) | 2009-06-02 | 2013-08-20 | Mitsubishi Electric Corporation | Refrigeration cycle apparatus |
CN105423613A (zh) * | 2015-12-23 | 2016-03-23 | 广西大学 | 一种机械增压式太阳能喷射制冷***及方法 |
Also Published As
Publication number | Publication date |
---|---|
JP2004150748A (ja) | 2004-05-27 |
EP1416231B1 (fr) | 2008-05-14 |
DK1416231T3 (da) | 2008-09-15 |
USRE43312E1 (en) | 2012-04-17 |
JP3863480B2 (ja) | 2006-12-27 |
DE60320918D1 (de) | 2008-06-26 |
US20040083751A1 (en) | 2004-05-06 |
ATE395564T1 (de) | 2008-05-15 |
US6880357B2 (en) | 2005-04-19 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
USRE43312E1 (en) | Refrigeration cycle apparatus | |
US6854283B2 (en) | Determining method of high pressure of refrigeration cycle apparatus | |
US6945066B2 (en) | Refrigeration cycle apparatus | |
JP4410980B2 (ja) | 冷凍空調装置 | |
JP3708536B1 (ja) | 冷凍サイクル装置およびその制御方法 | |
JP4321095B2 (ja) | 冷凍サイクル装置 | |
JP3811116B2 (ja) | 冷凍サイクル装置 | |
JP5018724B2 (ja) | エジェクタ式冷凍サイクル | |
WO2009098899A1 (fr) | Système de réfrigération | |
JP4837150B2 (ja) | 冷凍サイクル装置 | |
JP3870951B2 (ja) | 冷凍サイクル装置およびその制御方法 | |
JP2007212024A (ja) | 冷凍サイクル装置および冷凍サイクル装置の制御方法 | |
JP4901916B2 (ja) | 冷凍空調装置 | |
JP3863555B2 (ja) | 冷凍サイクル装置 | |
JP2004150749A (ja) | 冷凍サイクル装置 | |
JP2006145144A (ja) | 冷凍サイクル装置 | |
EP1830143A2 (fr) | Circuit de réfrigération | |
JP2004138333A (ja) | 冷凍サイクル装置 | |
JP4644278B2 (ja) | 冷凍サイクル装置 | |
JP2005207649A (ja) | ヒートポンプ式給湯装置 | |
KR20010048821A (ko) | 2단압축 냉난방 겸용장치 |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
PUAI | Public reference made under article 153(3) epc to a published international application that has entered the european phase |
Free format text: ORIGINAL CODE: 0009012 |
|
AK | Designated contracting states |
Kind code of ref document: A1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR |
|
AX | Request for extension of the european patent |
Extension state: AL LT LV MK |
|
17P | Request for examination filed |
Effective date: 20040907 |
|
AKX | Designation fees paid |
Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR |
|
17Q | First examination report despatched |
Effective date: 20070705 |
|
GRAP | Despatch of communication of intention to grant a patent |
Free format text: ORIGINAL CODE: EPIDOSNIGR1 |
|
GRAS | Grant fee paid |
Free format text: ORIGINAL CODE: EPIDOSNIGR3 |
|
GRAA | (expected) grant |
Free format text: ORIGINAL CODE: 0009210 |
|
AK | Designated contracting states |
Kind code of ref document: B1 Designated state(s): AT BE BG CH CY CZ DE DK EE ES FI FR GB GR HU IE IT LI LU MC NL PT RO SE SI SK TR |
|
REG | Reference to a national code |
Ref country code: GB Ref legal event code: FG4D |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: EP |
|
REG | Reference to a national code |
Ref country code: IE Ref legal event code: FG4D Free format text: LANGUAGE OF EP DOCUMENT: FRENCH |
|
REF | Corresponds to: |
Ref document number: 60320918 Country of ref document: DE Date of ref document: 20080626 Kind code of ref document: P |
|
REG | Reference to a national code |
Ref country code: DK Ref legal event code: T3 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: ES Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080825 Ref country code: FI Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 |
|
RAP2 | Party data changed (patent owner data changed or rights of a patent transferred) |
Owner name: PANASONIC CORPORATION |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: AT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PFA Owner name: PANASONIC CORPORATION Free format text: MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD#1006, OAZA-KADOMA#KADOMA-SHI, OSAKA 571-8501 (JP) -TRANSFER TO- PANASONIC CORPORATION#1006, OAZA KADOMA, KADOMA-SHI#OSAKA 571-8501 (JP) |
|
NLT2 | Nl: modifications (of names), taken from the european patent patent bulletin |
Owner name: PANASONIC CORPORATION Effective date: 20081119 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CZ Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 Ref country code: PT Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081014 Ref country code: SE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080814 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: SK Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 Ref country code: RO Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 |
|
PLBE | No opposition filed within time limit |
Free format text: ORIGINAL CODE: 0009261 |
|
STAA | Information on the status of an ep patent application or granted ep patent |
Free format text: STATUS: NO OPPOSITION FILED WITHIN TIME LIMIT |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: MC Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080831 |
|
REG | Reference to a national code |
Ref country code: CH Ref legal event code: PL |
|
26N | No opposition filed |
Effective date: 20090217 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: EE Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 Ref country code: BG Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080814 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: CH Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080831 Ref country code: LI Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080827 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: HU Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20081115 Ref country code: LU Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20080827 Ref country code: CY Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: TR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080514 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GR Free format text: LAPSE BECAUSE OF FAILURE TO SUBMIT A TRANSLATION OF THE DESCRIPTION OR TO PAY THE FEE WITHIN THE PRESCRIBED TIME-LIMIT Effective date: 20080815 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: BE Payment date: 20110812 Year of fee payment: 9 Ref country code: NL Payment date: 20110823 Year of fee payment: 9 |
|
BERE | Be: lapsed |
Owner name: MATSUSHITA ELECTRIC INDUSTRIAL CO., LTD Effective date: 20120831 |
|
REG | Reference to a national code |
Ref country code: NL Ref legal event code: V1 Effective date: 20130301 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: NL Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20130301 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: BE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20120831 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DK Payment date: 20130812 Year of fee payment: 11 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: FR Payment date: 20130808 Year of fee payment: 11 Ref country code: GB Payment date: 20130821 Year of fee payment: 11 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: IT Payment date: 20130819 Year of fee payment: 11 |
|
REG | Reference to a national code |
Ref country code: DK Ref legal event code: EBP Effective date: 20140831 |
|
GBPC | Gb: european patent ceased through non-payment of renewal fee |
Effective date: 20140827 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: IT Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140827 |
|
REG | Reference to a national code |
Ref country code: FR Ref legal event code: ST Effective date: 20150430 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: GB Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140827 Ref country code: DK Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140831 |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: FR Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20140901 |
|
PGFP | Annual fee paid to national office [announced via postgrant information from national office to epo] |
Ref country code: DE Payment date: 20180814 Year of fee payment: 16 |
|
REG | Reference to a national code |
Ref country code: DE Ref legal event code: R119 Ref document number: 60320918 Country of ref document: DE |
|
PG25 | Lapsed in a contracting state [announced via postgrant information from national office to epo] |
Ref country code: DE Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES Effective date: 20200303 |